Piston mechanism with diverging pistons

ABSTRACT

A piston mechanism comprises a crankcase, a crankshaft with three crankpins, a cylinder with diverging pistons defining working chambers having inlet and outlet openings, and two connecting members, one of which cooperates with the middle crankpin and the other with the two outer crankpins. In the body of the cylinder there are guide channels provided, in which connecting rods are arranged in alternating sequence, which are attached to one or the other connecting member by their bases, forming two synchronous groups of connecting rods. The guide channels are provided with through-cuts in the working surface of the cylinder with outlets into its cavity so that the faces of the connecting rods of the synchronous groups facing the cavity of the cylinder form movable parts of its working surface. The pistons are attached by their peripheries to the lateral faces of the connecting rods of one or the other synchronous group sequentially and spaced from each other, forming two movable rigid carcasses inserted in one another, moving in opposite directions.

CROSS REFERENCE TO RELATED APPLICATIONS

This application is entitled to the benefit of and incorporates byreference essential subject matter disclosed in International PatentApplication No. PCT/KZ2004/000002 filed on Mar. 11, 2004 and KazakhstanPatent Application No. 2003/0411.1 filed Mar. 26, 2003.

FIELD OF THE INVENTION

The invention relates to machine engineering, particularly to pistonmechanisms for direct transformation of energy of a working fluid (gasor steam) into mechanical energy or re-transformation of mechanicalenergy into the energy of a working fluid, and can be utilized in theconstruction and manufacturing of engines, compressors, hydraulicbuffers and the like.

BACKGROUND OF THE INVENTION

A two-stroke engine is known having divergent pistons, the inventor ofwhich is the applicant of the present application, which pistonmechanism comprises a cylinder in which pistons are arranged oppositeeach other, forming working chambers, the pistons being joined by twopairs of rods in two groups having an opposite direction of movement.Pistons of one of the directions of movement are firmly attached on eachpair of rods and spaced from one another, alternating with pistons ofthe opposite direction of movement. The rods of one group of pistons runthrough the pistons of the other group and vice versa. These rodscooperate with three crankpins of a crankshaft via links. Two outer rodsfor the pistons of one direction of movement are joined with two outercrankpins, while two inner rods for the pistons of the oppositedirection of movement are joined with a middle crankpin (see Germanapplication DE 3237858, Class F 01B 3/00, F 04B 27/00, 1984 r.).

The advantage of said piston mechanism lies in its ability to increasethe effectiveness of its work by a provision of working chambers fromboth sides of each piston, which allows a twofold increase of theeffective capacity, and also by the connection of the rods with threecrankpins of the crankshaft, which allows the pistons of the samedirection to work synchronized and parallel to one another.

However, a major shortcoming of this design is the problem of sealingthe rods in the regions where they run through the pistons of theopposite direction of movement. A lack of effective sealing results inleakage of the working chambers and decreases the reliability of thepiston mechanism as a whole. Moreover the cross movement of the rods andpistons taking place in this arrangement increases the wear of thecylinder walls and disrupts the evenness of the piston movement, whichis disadvantageous for the working characteristics of the pistonmechanism.

A two-stroke engine having divergent pistons is known, the inventor ofwhich is identical with the applicant of the present invention, whereintwo opposite cylinders are arranged along a common axis. The pistonmechanism of each cylinder comprises two divergent pistons acting on acommon crankshaft directly by power elements (connecting rods). Thecrankshaft comprises two basis pins and three crankpins, the two pistonsadjacent to the crankshaft acting on the middle crankpin and the twopistons spaced from the crankshaft acting on the two outer ones. Thepistons of the same direction of movement adjacent to the crankshaft arefirmly attached to one another by a hinge guiding a slide bar joined tothe middle crankpin. The pistons spaced from the crankshaft are joinedto the outer crankpins by links (see German patent DE 4135386, Class F02B 75/28, 75/32, 1992 r.).

The advantage of this technical solution is the replacement of rods bypower elements—connecting rods and a slide bar directly acting on thecrankshaft and outside the borders of the working cavity of thecylinder. Thus it becomes possible to house a second piston in eachcylinder. This exchange of the piston rods of one direction in favour ofconnecting rods makes it possible to seal the joint of thecylinder-piston system. The suggested two-stroke engine is characterisedby its compactness, low weight of the construction, the possibility touse multiple cylinders and low manufacturing costs.

The disadvantage of said two-stroke engine having divergent pistons isits marked friction of the hinge, which necessitates a frequentexchange.

A two-stroke engine with divergent pistons is known having a pistonmechanism comprising opposite cylinders with a stepped inner cavityhaving inlet and outlet openings and two pistons meeting each other ineach of them, and a crankshaft with three crankpins. Both outercrankpins are joined with a sliding sleeve (an outer connecting member)by a link, wherein the sliding sleeve slides through the cylinder bodylike on a guide rail and is joined with the pistons spaced from thecrankshaft by a synchronised group of connecting rods. These connectingrods are arranged so that they can move back and forth in guidingchannels arranged in the cylinder body parallel to its axis. The middlecrankpin is joined to the pistons adjacent to the crankshaft through atleast one link and an internal connecting member. The internalconnecting member is disposed in the cavity of the cylinder and isintegral with the pistons with apertures for the crankshaft to passthrough and move freely (see patent DE 19503444, F 02B 75/32, F 02B25/10, 1998).

The advantage of said known piston mechanism is that the piston rods ofone direction of movement are replaced by a group of connecting rodsmoving in synchronicity together with one connecting member in one case,and the connection of the pistons of the opposite direction of movementdirectly with the other connecting member, allowing a linear synchronousmovement of the pistons in both cylinders in another case. By linkingthe connecting members and the crankshaft, the wear of the connectinghinge mechanism and the basic bearings lessens. In any position, thecrankshaft is only loaded with the differing force of both resultants,the periodically activated forces of gas and mass on the inner and outercrankpins of the crankshaft. This positive effect multiplies as thenumber of revolutions of the engine increases.

A disadvantage of said technical solution lies in the different types ofthe outer and inner connecting members, which makes the design morecomplex and increases the dimensions and the weight of the mechanismwhile the kinetic connection of the pistons with the connecting membersis difficult. The construction must be manufactured with greatexactness. The problem of arranging more than two diverging pistons inone cylinder remains unsolved to date.

BRIEF SUMMARY OF THE INVENTION

The task which the present invention intends to solve is to create a newpiston mechanism which is efficient, reliably working, simple inmanufacturing and having a wide range of applications, and whichcontains little metal and is low in costs. Other objectives andadvantages of the present invention will become evident from thedescription and drawings.

The technical result is an increase of the specific capacity of thepiston mechanism by arranging a number of diverging pistons in onecylinder, which form working chambers between them, in which differentstrokes of independent working cycles are carried out simultaneously.

The task is solved in that in the piston mechanism with divergentpistons comprises a crankcase with a crankshaft, a cylinder with inletand outlet openings and at least two pistons directed in oppositedirections, and connecting members cooperating with three crankpins ofthe crankshaft, wherein one of the connecting members is joined to themiddle crankpin and the other is joined to the two outer crankpins,wherein at least one piston is firmly attached to connecting rods, thebases of which are firmly attached to one of the connecting members andlocated in guiding channels arranged in the cylinder body parallel toits axis, forming a synchronous group of connecting rods with adirection of movement corresponding to said connecting member, whereinthe cylinder additionally comprises connecting rods which are firmlyattached to at least one oppositely directed piston, while their basesare firmly attached to another connecting member, and which are locatedin additional guide channels formed in the cylinder body parallel to theknown guide channels in alternating sequence, forming anothersynchronous group of connecting rods having a direction of movementcorresponding to the other connecting member, wherein all guide channelsare arranged with through-cuts in the working surface of the cylinderwith outlets into its cavity so that lateral faces of the connectingrods of the synchronous groups of different directions facing the cavityof the cylinder form moving parts of its working surface, wherein thepistons are sequentially fastened by their periphery at the lateralfaces of the connecting rods of the different synchronous groups formingworking chambers between them, and the connecting members are locatedbetween the crankshaft and the piston adjacent to it; the connectingmembers are provided in the shape of the inner and, with a centralopening, the outer connecting members, which can freely move in oneanother so that the outline of the inner connecting member repeats theoutline of the central opening of the outer connecting member; the innerconnecting member is provided in the shape of two plates attached to oneanother, the lower one with a stand and the upper one with radial cutsaround the periphery for the connecting rod of the synchronous group ofsaid connecting member, which are attached to the lower plate by theirbases, and with recesses between said connecting rods in both plates forthe connecting rod of the other synchronous group; the outer connectingmember has the shape of two multi-lateral plates with an oval formattached to one another at their tops with central apertures, whereinthe lower one with two diametric stands and the upper one with radialcuts following the outline of the central aperture for the connectingrod of the synchronous group of said connecting member, attached to thelower plate by their bases, and with recesses between said connectingrods in both plates for the connecting rod of the other synchronousgroup; the inner connecting member is joined to the middle crankpin ofthe crankshaft; the outer connecting member is joined to two outercrankpins of the crankshaft; the inner connecting member is joined tothe middle crankpin of the crankshaft via a central crank-hinge frame;the outer connecting member is joined to two outer crankpins of thecrankshaft via lateral crank-hinge frames; the crank-hinge frames areeach made in the form of a separated rectangular outline with a standand a slide bar disposed in the outline for free translational movement,holding a corresponding crankpin of the crankshaft; the stand of thecentral crank-hinge frame is joined with the stand of the innerconnecting member through a pin; each of the stands of the lateralcrank-hinge frames is joined with the corresponding stand of the outerconnecting member via a pin; the crank-hinge frames are disposed betweenguiding plates arranged in the crankcase; the inner connecting member isjoined to the middle crankpin of the crankshaft via the central link;the outer connecting member is joined to the outer crankpins of thecrankshaft via the lateral links; the central link is joined to theinner connecting member via a pin; each of the lateral links is joinedto the corresponding stand of the outer connecting member via a pin; onthe lateral faces of the connecting rods of the synchronous group of theinner connecting member facing the cylinder cavity three protrusions forattaching the pistons of one direction of movement are formed; on thelateral faces of the connecting rods of the synchronous group of theouter connecting member facing the cylinder cavity two protrusions forattaching the pistons of the opposite direction of movement are formed;the protrusions on the connecting rods of the synchronous group of theouter connecting member are disposed between the protrusions on theconnecting rods of the synchronous group of the inner connecting member;the protrusions on the connecting rods of one synchronous group aredisposed at equal distances from one another which is equal to thedistance between the protrusions on the connecting rods of the othersynchronous group; the protrusions on the connecting rods of bothsynchronous groups are widening, the area of their cross sectionincreasing; on the wide faces of the connecting rods of both synchronousgroups from the side of their lateral faces disposed furthest away fromthe cylinder axis there are shoulders for the guide channels; theshoulders are formed continuously; the shoulders are interrupted; thewidths of the wide faces of the connecting rods of both synchronousgroups in a radial direction, not considering the shoulders, exceeds thethickness of the connecting rods by no less than two times; the crosssection of the connecting rods corresponds to the cross section of theguide channels; the connecting rods are arranged in the guide channelshaving a gap of less than 0.02 mm; the pistons have annular engaginggrooves for the protrusions of the connecting rod of the synchronousgroups; the pistons have annular grooves for the sealing rings; thepistons are shortened; the pistons are additionally attached to theprotrusions of the connecting rods of both synchronous groups by bolts;the guide channels for the connecting rods of both synchronous groupscover the entire length of the working cylinder; the guide channels forthe connecting rods of the synchronous groups are shortened; the guidechannels have a T-shaped cross section profile; the guide channels forthe connecting rods of the different synchronous groups alternate witheach other by one guide channel; the guide channels for the connectingrods of the different synchronous groups alternate with each other bytwo guide channels; in the cylinder body at equal distances from oneanother the guide channels are formed; the through-cuts in the guidechannels cover their entire lengths; the inlet and outlet openings aredisposed in central cross sections of the working chambers formed by twodiverging pistons; the working chambers formed by the diverging pistonshave the same height; the working chamber formed by one outer piston hasa height which is two times smaller than the working chambers formed bythe diverging pistons; the inlet and outlet openings are disposed in theupper part of the working chamber formed by one outer piston; the inletand outlet openings are arranged in spaces between the guide channels;the cylinder has an adjustable lid disposed in the crankcase; thecrankcase has technical apertures; the cylinder has a lid; the cylinderhas spark plugs in the working chambers.

The claimed invention differs from the most pertinent prior art in thatthe cylinder additionally comprises connecting rods which are firmlyattached to at least one piston moving in the opposite direction, andtheir bases are attached to the other connecting member, and aredisposed in additional guide channels formed in the cylinder bodyparallel to the known guide channels in alternating sequence, forming asynchronous group of connecting rods of the other connecting member,wherein all guide channels have through-cuts in the working surface ofthe cylinder with outlets into its cavity so that the lateral faces ofthe connecting rods of the synchronous groups of different directionsfacing the cavity of the cylinder form movable parts of its workingsurface, wherein the pistons are sequentially attached by theirperipheries to the lateral faces of the connecting rods of the differentsynchronous groups forming working chambers between them.

Each of these features is essential, and taken together they aresufficient for solving the pertinent task.

The arrangement of the connecting members between the crankshaft and thepiston adjacent thereto; the connecting members being provided as aninner, and, with a central opening, an outer connecting member for freemovement within one another so that the outline of the inner connectingmember repeats the outline of the central opening of the outerconnecting member; the inner connecting member having the form of twoplates attached to one another, the lower one with a stand and the upperone with radial cuts around the periphery for the connecting rod of thesynchronous group of said connecting member, attached to the lower plateby their bases and having recesses between these connecting rods in bothplates for the connecting rod of the other synchronous group; the outerconnecting member having the form of two multi-sided plates beingrounded to an oval at their tops and attached to one another withcentral openings, the lower one with two diametric stands and the upperone with radial cuts following the outline of the central opening forthe connecting rod of the synchronous group of said connecting memberattached on the lower plate by their bases, and having recesses betweensaid connecting rods in both plates for the connecting rod of the othersynchronous group; connecting the inner connecting member with themiddle crankpin of the crankshaft; connecting the outer connectingmember with two outer crankpins of the crankshaft; connecting the innerconnecting member with a middle crankpin of the crankshaft through acentral crank-hinge frame; connecting the outer connecting member withthe outer crankpins of the crankshaft through lateral crank-hingeframes; the crank-hinge frames each having the form of a separatedrectangular outline with a stand and with a slide bar disposed withinthe outline for free translational movement which holds thecorresponding crankpin of the crankshaft; connecting the stand of thecentral crank-hinge frame with the stand of the inner connecting membervia a pin; connecting each of the stands of the lateral crank-hingeframes with the corresponding stand of the outer connecting member via apin; disposing the crank-hinge frames between the guide plates disposedin the crankcase; connecting the inner connecting member with the middlecrankpin of the crankshaft via a central link; connecting the outerconnecting member with the outer crankpins of the crankshaft via laterallinks; connecting the central link with the stand of the innerconnecting member via a pin; connecting each of the lateral links withthe corresponding stand of the outer connecting member via a pin;arranging three protrusions for attaching the pistons of one directionof movement on the connecting rods of the synchronous group of the innerconnecting member on the lateral faces, facing the cylinder cavity;arranging two protrusions for attaching the pistons of the oppositedirection of movement on the connecting rods of the synchronous group ofthe outer connecting member on the lateral faces, facing the cylindercavity; arranging the protrusions on the connecting rods of thesynchronous group of the outer connecting member between the protrusionson the connecting rods of the synchronous group of the inner connectingmember; arranging the protrusions on the connecting rods of onesynchronous group at equal distances from one another and equaldistances between the protrusions on the connecting rods of the othersynchronous group; widening the protrusions on the connecting rods ofboth synchronous groups so that the area of their cross section isenlarged; providing both synchronous groups on the wide faces from theside of their lateral faces which are furthest away from the cylinderaxis with shoulders for the guide channels; making the shoulderscontinuous; making the shoulders interrupted; the width of the widefaces of the connecting rods of both synchronous groups in a radialdirection exceeding the thickness of the connecting rods by no less thantwo times without considering the shoulders; correspondence of the crosssection of the connecting rods to the cross section of the guidechannels; arrangement of the connecting rod in the guide channels with agap of less than 0.02 mm; providing the pistons with annular engaginggrooves for the protrusions of the connecting rods of the synchronousgroups; providing the pistons with annular grooves for the sealingrings; shortening the pistons; additionally securing the pistons on theprotrusions of the connecting rods of both synchronous groups by bolts;arranging the guide channels for the connecting rods of both synchronousgroups over the entire length of the working cylinder; shortening theguide channels for the connecting rods of the synchronous groups; theguide channels having a T-shaped cross section profile; alternation ofthe guide channels with each other for the connecting rods of thedifferent synchronous groups by one guide channel; alternation of theguide channels with each other for the connecting rods of the differentsynchronous groups by two guide channels; forming the guide channels inthe cylinder body at equal distances from one another; arrangingthrough-cuts in the guide channels along their entire length; disposingthe inlet and outlet openings in the central sections of the workingchambers formed by two diverging pistons; equal height with respect toeach other of the working chambers formed by the diverging pistons;making the working chamber formed by one outer piston two times smallerin height than the working chambers formed by the diverging pistons;disposing the inlet and outlet openings in the upper part of the workingchamber formed by one outer piston; disposing the inlet and outletopenings in spaces between the guide channels; providing the cylinderwith an adjustable lid disposed in the crankcase; providing thecrankcase with technical apertures; providing the cylinder with a lid;providing the cylinder with spark plugs in the working chambers are thefeatures characterising the proposed invention in special embodiments.

The presence of the additional connecting rods which are firmly attachedto at least one oppositely directed piston, and are firmly attached tothe other connecting member by their bases, allows to create anothersynchronous group of connecting rods of the opposite direction ofmovement, which is identical with the known synchronous group ofconnecting rods, which allows the use of equal parts and asimplification of their manufacture while the possibilities of kineticconnections of the pistons with the connecting members are increased.

The arrangement of the additional connecting rods in the additionalguide channels disposed in the cylinder body parallel to the known guidechannels in an alternating manner allows the disposal of a secondsynchronous group of connecting rods of opposite direction of movementexactly like the known group of connecting rods and to lessen anoverload of the working cavity of the cylinder, which allows asimplification of the design of the piston mechanism, a reduction of itsdimensions and a more efficient use of the working cavity of thecylinder.

Providing all guide channels with through-cuts in the working surface ofthe cylinder with outlets into its cavity allows a disposal of theconnecting rods of both synchronous groups in the guide channels so thattheir lateral faces facing the cylinder cavity form movable parts of itsworking surface with an opposite direction of movement, which allows afirm attachment of the pistons immediately by their peripheries with themovable parts of the working surface of the cylinder. Such an attachmentof the pistons of both directions of movement by their peripheries doesaway with all restrictions concerning their arrangement in one cylinderin the necessary number.

The sequential arrangement of the pistons on the synchronous connectingrods of the different groups does away with restrictions concerning thearrangement of working chambers in the necessary number in one cylinderbetween diverging pistons, which simultaneously carry out differentstrokes of independent working cycles.

The complete claimed features make it possible to obtain a pistonmechanism characterised by its increased specific capacity, low weight,compactness, simple design and construction, low manufacturing costs,increased reliability, long work life, and with a greater range ofapplications.

BRIEF DESCRIPTION OF THE DRAWINGS

The essential features of the present invention will become clear fromthe following description making reference to the accompanying drawings.

FIG. 1 is a longitudinal sectional view of the piston mechanism, on theleft of the axis: the pistons of one and the other synchronous groups ofconnecting rods at maximum displacement along the axis in oppositedirections and being at opposite dead centers, and on the right of theaxis: the same, one stroke later, according to the present invention;

FIG. 2 is a longitudinal sectional view in the plane 2—2 of FIG. 1, onthe left of the axis: the position of the pistons analogous to theposition of the pistons on the left of the axis in FIG. 1, on the rightof the axis: one stroke later;

FIG. 3 is a cross sectional view in the plane 3—3 of FIG. 1;

FIG. 4 is a cross sectional view in the plane 4—4 of FIG. 1 with theadjustable lid removed, on the left of the axis: with the connectingrods, pistons and outer connecting member removed, on the right of theaxis: with the inner connecting member removed;

FIG. 5 is a cross sectional view of the cylinder of the pistonmechanism;

FIG. 6 is a side view of a connecting rod of a synchronous group ofconnecting rods, firmly attached to the inner connecting member;

FIG. 7 is a side view of a connecting rod of a synchronous group ofconnecting rods, firmly attached to the outer connecting member;

FIG. 8 is a front view of the middle crank-hinge frame in an assembledstate, on the left of the axis: in longitudinal section;

FIG. 9 is a view in the plane 9—9 in FIG. 8, on the left of the axis: incross section;

FIG. 10 is a side view of a connecting rod of a synchronous group ofconnecting rods, firmly attached to the inner connecting member, avariant of the connecting rod with widening protrusions and interruptedshoulders;

FIG. 11 is a front view of the connecting rod of FIG. 10;

FIG. 12 is a view from the end of the crank-hinge frame in the directionof arrow 12 shown in FIG. 8, on the left of the axis: in longitudinalview;

FIG. 13 is a side view of the piston, on the left of the axis: inlongitudinal section;

FIG. 14 is a cross sectional view in the plane 14—14 in FIG. 10;

FIG. 15 is a side view of the inner connecting member in assembled statewith connecting rods of a corresponding synchronous group;

FIG. 16 is a cross sectional view in the plane 16-16 in FIG. 15;

FIG. 17 is a side view of the outer connecting member in assembled statewith connecting rods of a corresponding synchronous group;

FIG. 18 is a cross sectional view in the plane 18—18 in FIG. 17.

DETAILED DESCRIPTION OF THE INVENTION

One embodiment is chosen as the preferred one of the proposed pistonmechanism for the example of a four-stroke internal combustion engine(ICE).

The piston mechanism (ICE) (see FIG. 1) comprises a cylinder 1 with anadjustable lid 2 attached on a removable insert 3 arranged in acrankcase 4. Pistons 5, 6 are arranged in the cylinder 1, while in thecrankcase 4 a crankshaft 7 is arranged disposed in bearing assemblies 8on bearings 9. Three pistons 5 and two pistons 6 form working chambers10, 11, 12, 13 between them with inlet 14 and outlet 15 openings (seeFIG. 2, 4) in the cross section of each of them. In the body of thecylinder 1 (see FIG. 5) two groups of guide channels 16, 17 are arrangedevenly in a circle parallel to its axis, with three channels in eachgroup. The guide channels 16, 17 alternate with one another. The guidechannels 16, 17 are provided over their entire length with through-cuts18 in the working surface of the cylinder 1 with outlets into itscavity. The guide channels 16, 17 have a T-shaped cross sectionalprofile. In the guide channels 16 connecting rods 19 are disposed (seeFIG. 3) for translational movement, and in the guide channels 17,connecting rods 20 are disposed in the same way. Each of the connectingrods 19, 20 faces the cavity of the cylinder 1 by its narrow lateralside 21 (see FIG. 6, 7) having the profile of the working surface of thecylinder 1 so that the lateral sides 21 of all connecting rods 19, 20form movable parts of its working surface. The narrow connecting rods19, 20, having sufficient width in the radial direction, can withstandhigh axial loads. They have sufficient flexibility in the crossdirection enabling them to be arranged in the long guide channels 16, 17with a gap of less than 0.02 mm providing the necessary seal of theworking chambers. To maintain the cylindrical configuration of theworking surface of the cylinder 1 in the movable parts providing asmooth transition of its the movable parts to the non-movable ones,shoulders 24 are formed on the wide lateral faces 22 of each of theconnecting rods 19, 20 from the side of the lateral face 23 which isfurthest away from the axis of the cylinder 1 for the profile of theguide channels 16, 17 preventing radial displacement of said connectingrods. The width of the lateral faces 22 of the connecting rods 19, 20without considering the shoulders 24 exceeds their thickness by no lessthan two times. On the lateral faces 21 of each connecting rod 19 (seeFIG. 6) three protrusions 25 of different height from its lower end arearranged for attaching three pistons 5, each around its periphery, onall connecting rods 19 on the corresponding level. On the lateral face21 (see FIG. 7) of each connecting rod 20 two protrusions 26 arearranged having different heights from its lower end for attaching twopistons 6, each around its periphery, on all connecting rods 20 at thecorresponding level. The distances between the protrusions 25, 26 ofeach connecting rod 19, 20 are equal to one another. The protrusions 26of the connecting rods 20 are arranged between the protrusions 25 of theconnecting rods 19 and take up a central position between them when thepistons 6 are located in a middle position between the correspondingpistons 5 (see FIG. 2).

The lower bases of the connecting rods 19 are firmly attached to theinner connecting member 27 (see FIG. 15, 16) forming one synchronousgroup of connecting rods 19, and the lower bases of the connecting rods20 are firmly attached to the outer connecting member 28 (see FIG. 17,18) forming the other synchronous group of connecting rods 20. The innerconnecting member 27 and the outer connecting member 28 (see FIG. 3) arearranged for free movement in each other so that the inner outline ofthe outer connecting member 28 repeats the outline of the innerconnecting member 27. They are disposed between the cylinder 1 and thecrankshaft 7 (see FIG. 1, 2).

The inner connecting member 27 (see FIG. 15, 16) has the form of twoplates attached to one another, the lower one 29 with a stand 30 and theupper one 31 with radial cuts 32 around the periphery for the connectingrod 19 and with recesses 33 between them in both plates for theconnecting rod 20. The connecting rods 19 are arranged with their baseson the lower plate 29. Their securing grips 34 are engaged between theplates 29, 31 by bolts 35.

The outer connecting member 28 (see FIG. 17, 18) has the form of twomulti-sided plates formed into an oval at their tops and attached to oneanother with central openings 36, the lower one 37 of them with twodiametric stands 38 and the upper one 39 with radial cuts 40 followingthe outline of the central opening 36 for the connecting rod 20 of thesynchronous group of this connecting member and with recesses 41 betweenthese connecting rods in both plates for the connecting rod 19 of theother synchronous group. The connecting rods 20 are positioned on thelower plate 37 by their bases. Their securing grips 42 are engagedbetween the plates 37, 39 by bolts 43.

When arranging the connecting members 27, 28 in one plane (see FIG. 2 tothe right of the axis), the basic working chambers 10, 11, 12, 13 areequal to each other in height. The upper piston 5 forms an additionalchamber 45 with the lid 44 of the cylinder 1, the height of which isequal to half the height of the basic working chambers 10, 11, 12, 13with the same position of the connecting members 27, 28, when theconnecting members 27, 28 are installed on one level.

On the peripheries of the lateral surfaces of the pistons 5, 6 (see FIG.13) there are annular engaging grooves 46 by which the pistons 5, 6 areattached firmly with pressure to the protrusions 25, 26 corresponding tothe connecting rods 19, 20. The attachment of each of the pistons 5, 6on three synchronous connecting rods 19 or 20 by their peripheriesfirmly stabilizes their vertical position and decreases the load on eachconnecting rod threefold. Such attachment allows a radial widening ofthe pistons 5, 6 displacing them along the corresponding protrusions 25,26 when they are heated and returning them into their initial positionwhen they cool down. On the side face of the pistons 5, 6 around theirperipheries on both sides from the annular engaging grooves 46, annulargrooves 47 are formed for sealing rings.

The inner connecting member 27 is joined with a middle crankpin 48 (seeFIG. 1) of the crankshaft 7 through a central crank-hinge frame 49, andthe outer connecting member 28 is joined with outer crankpins 50, 51 ofthe crankshaft 7 through lateral crank-hinge frames 52, 53. The centralcrank-hinge frame 49 is analogous to the lateral crank-hinge frames 52,53 and differs from them only by its reinforced structure since it isdesigned for a double load. Each of the crank-hinge frames 49, 52, 53(see FIGS. 8, 9, 12) is a frame having a respective slide bar 54arranged inside in the form of two cross bars 55 arranged on twosupports 56 with the aid of two coupling bolts 57. The upper cross bar55 has a stand 58 in its middle portion from the side of the cylinder 1.Each slide bar 54 is a thick rectangular apertured plate with a centralopening 59 for one of the crankpins 48, 50, 51 of the crankshaft 7. Bothconstructive parts 60 of each slide bar 54 have protrusions 61 forsecuring said parts with one another by bolts 62 together at thecorresponding crankpin 48, 50, 51.

The stand 58 of the central crank-hinge frame 49 is pivotally joined tothe stand 30 by a pin 63 (see FIG. 2), which stand 30 is provided in themiddle portion of the lower plate 29 of the inner connecting member 27.The stands 58 of the lateral crank-hinge frames 52, 53 are eachpivotally joined by the pins 63 to one of two diametric stands 38 on thelower plate 37 of the outer connecting member 28. Thus, the middlecrankpin 48 of the crankshaft 7 is joined to the inner connecting member27 by the central crank-hinge frame 49, while two outer crankpins 50, 51are joined to the outer connecting member 28 by the lateral crank-hingeframes 52, 53. In such a kinetic joint the crank-hinge frames 49, 52, 53have a free rotating stage around the corresponding pin 63 in anyposition of the crankshaft 7. Stability of their position is obtained byguide plates 64 (see FIG. 2) and the regulating bolts 65 disposed in thecrankcase 4. On the walls of the cylinder 1 in the cross sections of theworking chambers 10, 11, 12, 13, spark plugs 66 are disposed. Under thelid 44 of the cylinder 1 in the additional working chamber 45, inlet andoutlet openings 67 resp. 68 are provided and a spark plug 66 is disposed(see FIG. 2).

In a not presented embodiment of the invention there is a variation ofthe opposite disposal of the cylinders 1. In this embodiment thecrank-hinge frames 49, 52, 53 are provided with two oppositely arrangedstands 58, which joined from two sides to the connecting members 27, 28of the oppositely arranged cylinders 1. The number of oppositelyarranged cylinders 1 depends on the required capacity of the internalcombustion engine.

In possible embodiments of the piston mechanism the overall number ofpistons 5, 6 can equal two or more.

There can be two or more synchronous connecting rods 19, 20 in eachgroup. The number of guide channels 16, 17 is defined in accordance withthe number of connecting rods 19, 20.

The connecting rods of the different synchronous groups 19, 20 canalternate with each other by one connecting rod or more. The guidechannels 16, 17 are provided for the corresponding connecting rods 19,20.

The connecting rods 19 can be provided with widening protrusions 25 (seeFIGS. 10, 11, 14) having a greater width, with a more evenlydistribution of forces on them along their height and along the linewhere they are joined to the connecting rods 19. The connecting rods 20are provided in an analogous manner.

The guide channels 16, 17 can be shortened for limiting the movement ofthe corresponding connecting rods 19, 20 (see FIG. 1).

The connecting rods 19 can be provided with interrupted shoulders 24with a corresponding increase of their flexibility. The connecting rods20 are provided in an analogous manner.

The connecting members 27, 28 can be joined with the correspondingcrankpins 48, 50, 51 of the crankshaft 7 by links.

The pistons 5, 6 can be additionally attached to the protrusions of thecorresponding connecting rods by bolts.

The action of the above described embodiment of the piston mechanism forthe example of a four-stroke ICE evidently shows the wide range ofpossibilities of the proposed invention. In the system of a four-strokeICE an independent working cycle is repeated continuously in eachworking chamber 10, 11, 12, 13, including the sequence of the fourstrokes: The first stroke is the working stroke, the second stroke isthe outlet stroke, the third stroke is the inlet stroke, the fourthstroke is the compression stroke involving a determined mass of workingfluid (a fuel mix or combustion products). The initial state of theworking chambers 10, 11, 12, 13 (see FIG. 1 to the left of the axis) issuch that all chambers are prepared so that the following strokes can becompleted therein simultaneously: A working stroke in working chamber10, a compression stroke in working chamber 11, an inlet stroke inworking chamber 12, an outlet stroke in working chamber 13, whichpertain to independent working cycles of the corresponding workingchambers, displaced by one stroke per working chamber in the indicatedsequence.

In the initial state the working chamber 10 is filled with compressedfuel mix, and when high voltage is energized on the spark plug 66disposed in said chamber, the fuel mix combusts. An increase of thepressure in the working chamber 10 during burning of the fuel mixresults in a stepwise movement of the pistons 5, 6 in oppositedirections, transferring force from them onto the crankpins 48, 50, 51of the crankshaft 7. This force is transferred through correspondinggroups of synchronous connecting rods 19, 20, the connecting members 27,28, the crank-hinge frames 49, 52, 53 and the slide bars 54. Thesynchronous group of connecting rods 19, 20 move in the guide channels16, 17 in opposite directions. As a result, in the working chamber 10 aworking operation is completed. The crankshaft 7 does a half revolution,the first stroke (working operation) of a full working cycle of theworking chamber 10 is completed. Simultaneously in the working chambers11, 12, 13 the following strokes are completed, respectively: The fourthstroke (compression) in the working chamber 11, the third stroke (inlet)in the working chamber 12, the second stroke (outlet) in the workingchamber 13 of a full working cycle of each of said chambers. The pistons5, 6 (see FIG. 1 to the right of the axis) are in opposite positions inthe working cylinder 1. The basic working chambers 10, 11, 12, 13 are,respectively, prepared for the completion of the following strokes:Outlet (second stroke) in working chamber 10, working operation (firststroke) in working chamber 11, compression (fourth stroke) in workingchamber 12, inlet (third stroke) in working chamber 13.

In this situation the compressed fuel mix fills the working chamber 11,and after high voltage is energized on the spark plug 66 disposed insaid chamber, a combustion of the fuel mix takes place therein in ananalogous manner, and the working operation is completed. The crankshaft7 does another half revolution, the first stroke (working operation) ofthe full working cycle of chamber 11 is completed. Simultaneously in theworking chambers 12, 13, 10 the following strokes are completed,respectively: The fourth stroke (compression) in working chamber 12, thethird stroke (inlet) in working chamber 13, the second stroke (outlet)in working chamber 10, of a full working cycle of each of said chambers.The pistons 5, 6 (see FIG. 1 to the left of the axis) occupy theirinitial position in the working cylinder 1. As a result, the basicworking chambers 10, 11, 12, 13 are prepared for, respectively, thecompletion of the following strokes: Inlet (third stroke) in workingchamber 10, outlet (second stroke) in working chamber 11, workingoperation (first stroke) in working chamber 12, compression (fourthstroke) in working chamber 13.

In this situation the compressed fuel mix fills the working chamber 12,and a working operation is completed therein in an analogous manner witha corresponding turn of the crankshaft 7 by another half revolution. Thefirst stroke (working operation) of a full working cycle of the workingchamber 12 is completed. Simultaneously, in the working chambers 13, 10,11 the following strokes are completed, respectively: The fourth stroke(compression) in working chamber 13, the third stroke (inlet) in workingchamber 10, the second stroke (outlet) in working chamber 11, of a fullworking cycle of each of said chambers. The pistons 5, 6 (see FIG. 1 tothe right of the axis) again occupy a position opposite to their initialposition in the cylinder 1. The working chambers 10, 11, 12, 13 are,respectively, prepared for the completion of the following strokes:Compression (fourth stroke) in working chamber 10, inlet (third stroke)in working chamber 11, outlet (second stroke) in working chamber 12,working operation (first stroke) in working chamber 13.

In this situation the working chamber 13 is filled with compressed fuelmix. After completion of the working operation therein in an analogousmanner with a corresponding turn of the crankshaft 7 by another halfrevolution, the first stroke (working operation) of the full workingcycle of chamber 13 is completed. Simultaneously, in the workingchambers 10, 11, 12 the following strokes are completed, respectively:The fourth stroke (compression) in working chamber 10, the third stroke(inlet) in working chamber 11, the second stroke (outlet) in workingchamber 12, of a full working cycle of each of said chambers. As aresult, after the sequential completion of the first stroke in allworking chambers 10, 11, 12, 13 of a full working cycle of each of saidchambers, the crankshaft has completed two full revolutions, the pistons5, 6 (see FIG. 1 to the left of the axis) occupy their initial positionwhere they were at the very beginning, and the working chambers 10, 11,12, 13 are again prepared for the completion of the following strokesrespectively: Working operation (first stroke) in working chamber 10,compression (fourth stroke) in working chamber 11, inlet (third stroke)in working chamber 12, outlet (second stroke) in working chamber 13. Inthis situation the working chamber 10 is prepared for the second and thefollowing working cycles, and the working chambers 11, 12, 13 for thecompletion of the previous cycle.

The supply of fuel mix into the working chambers 10, 11, 12, 13 iscarried out at the inlet strokes through inlet openings 14. The removalof exhaust gases from the working chambers 10, 11, 12, 13 is carried outat the outlet strokes through outlet openings 15. In the workingoperation and compression stroke modes the inlet openings 14 and theoutlet openings 15 are closed.

An additional working chamber 45 is formed by one piston. Its height istwo times smaller than the height of the working chambers 10, 11, 12,13. It can be analogously used to increase the output capacity of thepiston mechanism used in a type of ICE. The supply of fuel mix into theadditional working chamber 45 is carried out at the inlet strokesthrough an inlet opening 67. The removal of exhaust gases is carried outat the outlet strokes through outlet openings 68. In the workingoperation and compression stroke modes the inlet openings 67 and theoutlet openings 68 are closed. The working mode of the additionalworking chamber 45 is not linked to the modes of the working chambers10, 11, 12, 13, therefore its use results in some disruption of the loadsymmetry in the kinetic scheme of the ICE. Since the capacity of theadditional working chamber 45 is two times lower than the capacity ofany of the working chambers 10, 11, 12, 13, it does not exert anyconsiderable influence on the dimensions and strength characteristics ofthe elements of the piston mechanism.

In the proposed piston mechanism, for an effective use of the cylindercavity on both sides of all pistons except the lowermost, its effectiveworking volume and correspondingly the capacity are increased by 1.9times, while without considering the additional working chamber thefigure is 1.8 times. Its working cycles are displaced in adjacentworking chambers by one stroke per phase, thus for every turn of thecrankshaft by a half revolution, the working operation is completed inonly one of them. As a result, the increase of the number of workingchambers in one cylinder up to four does not cause an increase of themomentary load on the crankshaft. Therefore a short crankshaft withthree crankpins is used, designed for the force to which it is subjectedduring the operation of one piston. Consequently, in comparison to theknown four-cylinder piston mechanism of analogous capacity, thedimensions of the crankcase are decreased approximately threefold. As aresult, for an effective use of the cylinder cavity and for adisplacement of phases of the working cycles in the working chambers,the overall volume, and consequently also the weight of the pistonmechanism are decreased 2–3 fold.

An additional decrease of the volume and weight of the piston mechanismis caused by a decrease of the height of the pistons and their operationwith a corresponding decrease of the revolution radius of the crankpinsof the crankshaft as well as the load imparted on them, on theconnecting rods and the connecting members. The decrease of therevolution radius of the crankpins of the crankshaft allows an increaseof its revolutions. The arrangement of the opposite working cylinderresults in a doubling of the capacity of the piston mechanism.

The employment of diverging pistons leads to a redistribution of thework load evenly on the opposite crankpins of the crankshaft with amutual compensation of the overall load on the bearing assemblies. Thisincreases their lifetime and increases the reliability of the pistonmechanism. An increase in efficiency and working reliability of thepiston mechanism is caused additionally due to the essentially lessenedwear of the sealing rings. The sealing rings attach more tightly to thesynchronous connecting rods of their own group of pistons and totallyrely only on them due to their own elasticity, depending on theirrunning-in towards the immobile parts of the working surface of thecylinder and towards its movable parts formed by the synchronousconnecting rods of the oppositely oriented group of pistons. Thisresults in a deceleration and therefore in a prevention of wear of thesealing rings while their elasticity is almost entirely maintained. Dueto the axial symmetry of the load on the pistons and the stability ofthe position of the sealing rings in the annular grooves the wear of theside walls of said grooves and the sealing rings in the area where theycontact these walls is also prevented. Preferably, sealing rings withincreased elasticity are employed.

The temperature mode of the synchronous connecting rods does not differfrom the temperature mode of the cylinder walls. This allows theirplacement in long guide channels with a gap of less than 0.02 mm whilemaintaining the required demands on smooth operation and securingtightness of the working chambers. The described embodiment is toillustrate the essential features of the invention and does not limitthe scope of the invention in any way, which is defined by the claimsand can be carried out in other embodiments.

The construction of the piston mechanism is carried out in the followingorder. The crankshaft 7 is arranged in the crankcase 4 of the pistonmechanism. Thereafter the bearing assemblies 8 with the bearings 9 areinstalled, which support the crankshaft 7. On the crankpins 48, 50, 51of the crankshaft 7 the subsequent construction of the correspondingslide bars 54 and crank-hinge frames 49, 52, 53 is carried out. Thesealing rings are arranged on the pistons 5, 6 in their annular grooves47. The inner connecting member 27 is placed horizontally on the stand58 of the central crank-hinge frame 49 by a stand 30 on its lower plate29. The stands 30 and 58 are joined to each other by a pin 63. Theconnecting rods 19 are arranged in a circle by the securing grips 34 onthe lower plate 29 of the inner connecting member 27 in verticalposition arranged in the cuts 32 in the upper plate 31. Initially, twoconnecting rods 19 are arranged. Thereafter all five pistons 5, 6together with the sealing rings are stacked from the bottom upwards inthe required order, one by one. Thereafter the third connecting rod 19is arranged in the required position. During construction the securinggrips 34 of the connecting rods 19 are attached for stability betweenthe lower and the upper plates 29, 31 respectively by bolts 35 withlittle force. The pistons 5 are distributed by height using gaginginserts so that their annular engaging grooves 46 are positioned on thelevels of the corresponding protrusions 25 of the connecting rods 19.The pistons 6 are placed on the pistons 5 positioned underneath. Theprotrusions 25 are simultaneously inserted to some depth into theannular engaging grooves 46 of the pistons 5 for mutual fastening in therequired position, in groups of three on every connecting rod 19 in thesequence of these connecting rods, by applying a predetermined, evenlydistributed radial force on the corresponding connecting rod 19. Ifnecessary, a preliminary positioning of the protrusions 25 on thepistons 5 is carried out with weaker bolts 35. The protrusions 25,having been preliminarily fastened to the pistons 5, are arranged in theannular engaging grooves 46 of the pistons 5 to the full depthsynchronously and under pressure by simultaneously applying an equal,evenly distributed radial force on all connecting rods 19. Thereafterthe position of the securing grips 34 of the connecting rods 19 on theinner connecting member 27 and of the pistons 5 on the protrusions 25 iscorrected in accordance with the actual position of the connecting rods19 in the guide channels 16 by temporarily placing the working cylinder1 in them at maximum depth. The connecting rods 19 fasten on the innerconnecting member 27 by bolts 35 when the working cylinder 1 is placedon them. This fastening of the connecting rods 19 allows to maintain thesmoothness of their operation in the guide channels 16 withoutcorrecting their position with respect to the other members fastened tothem when the working cylinder 1 is moved back and forth many times.

Separately from the piston mechanism, a preliminary construction of theouter connecting member 28 with the connecting rods 20 is carried out.For this, said outer connecting member 28 is positioned horizontally.The connecting rods 20 are arranged in a circle on its lower plate 37 bythe securing grips 42 in a vertical position, placed in the cuts 40 ofthe upper plate 39 so that a channel for the pistons 5, 6 is maintainedbetween their protrusions 26. The securing grips 42 of the connectingrods 20 are fastened between the lower and upper plates 37, 39,respectively, with little force of the bolts 43. The crankshaft 7 isarranged so that its outer crankpins 50, 51 occupy the upper position,and the middle crankpin 48 with the slide bar 54 arranged thereon, thecentral crank-hinge frame 49 with the inner connecting member 27, theconnecting rods 19 and the pistons 5, 6 occupy the lower position. Theworking cylinder 1 is removed. The outer connecting member 28 assembledwith the connecting rods 20 is positioned horizontally on the stands 58of the lateral crank-hinge frames 52, 53 by diametric stands 38 on itslower plate 37. The inner connecting member 27 passes through itscentral opening 36 in the process of arranging the outer connectingmember. The corresponding stands 38 and 58 are joined to one another bypins 63. With a revolution of the crankshaft 7 the connecting members27, 28 are placed on one level. By the arrangement of corresponding gageinserts the non-fastened pistons 6 are distributed by height so thattheir annular engaging grooves 46 are positioned on the level of thecorresponding protrusions 26 of the connecting rods 20 of the outerconnecting member 28. Analogously with the protrusions 25 of theconnecting rods 19, the protrusions 26 are simultaneously inserted tosome depth into the annular engaging grooves 46 of the pistons 6 forfastening in the required position, in groups of two on every connectingrod 20 in the sequence of these connecting rods, by applying apredetermined, evenly distributed radial force on the correspondingconnecting rod 20. If necessary, a preliminary positioning of theprotrusions 26 on the pistons 6 is carried out with weaker bolts 43. Theprotrusions 26, having been preliminarily fastened to the pistons 6, arearranged in the annular engaging grooves 46 of the pistons 6 to the fulldepth synchronously and under pressure by simultaneously applying anequal, evenly distributed radial force on all connecting rods 20.Thereafter the position of the securing grips 42 of the connecting rods20 on the outer connecting member 28 and of the pistons 6 on theprotrusions 26 is corrected in accordance with the actual position ofthe connecting rods 20 in the guide channels 17 by temporarily placingthe working cylinder 1 in them at maximum depth. The connecting rods 20are fastened on the outer connecting member 28 by the bolts 43 when theworking cylinder 1 is placed on them. This fastening of the connectingrods 20 allows to maintain the smoothness of their operation in theguide channels 17, simultaneously maintaining the smoothness of theoperation of the connecting rods 19 in the guide channels 16, withoutsubsequently correcting the position of the connecting rods 19, 20 withrespect to the other members fastened to them when the working cylinder1 is moved back and forth many times.

The working cylinder 1 is removed and a removable insert 3 is fastenedon the crankcase 4 in an appropriate manner. Thereafter, the workingcylinder 1 is placed on the connecting rods 19, 20 at the requireddepth, and by its adjustable lid 2 is fastened on the removable insert 3in an appropriate manner. A rigid axial displacement of the crank-hingeframes 49, 52, 53 is made possible by corresponding guide plates 64using regulating bolts 65 for their correct placement. The regulation iscarried out at the turn of the crankshaft 7.

When the piston mechanism is provided without the removable insert 3,the adjustable lid 2 of the working cylinder 1 is placed immediately onthe crankcase 4. In this embodiment one or more technical apertures areprovided in the crankcase 4 of the working cylinder 1 for itsconstruction.

The advantage of said piston mechanism is that the required number ofoppositely directed pistons is arranged in the body of one cylinder,forming the corresponding number of working chambers, in which differentstrokes of independent working cycles are completed simultaneously.

The piston mechanism has an increased dynamic balance and a longerworking life with a lessened intensity of wear. It is light, simple, andfast to construct and deconstruct. Its weight is decreased by two tothree times, and its price is reduced by one and a half to two times.The use of the proposed piston mechanism with diverging pistonsincreases the specific capacity by a minimum of 1.8 times.

While the present invention has been illustrated and described withrespect to a particular embodiment thereof, it should be appreciated bythose of ordinary skill in the art that various modifications to thisinvention may be made without departing from the spirit and scope of thepresent invention.

1. A piston mechanism with diverging pistons comprising: a crankcasewith a crankshaft, a cylinder with inlet and outlet openings and atleast two pistons of opposite directions of movement, and connectingmembers interacting with three crankpins of, the crankshaft, wherein oneof the connecting members is joined with a middle crankpin and the otheris joined with two outer crankpins, wherein at least one piston isfirmly attached to connecting rods, which are rigidly fastened to one ofthe connecting members by their bases and are positioned in guidechannels provided in the cylinder parallel to its axis, forming asynchronous group of connecting rods with a direction of movementcorresponding to said connecting member, characterized in that thecylinder additionally comprises connecting rods which are firmlyattached to at least one of pistons of opposite direction of movement,and by their bases are attached to the other connecting member, and arepositioned in additional guide channels formed in the body of thecylinder parallel to abovementioned guide channels in alternatingsequence with them, forming another synchronous group of connecting rodswith a direction of movement corresponding to the other connectingmember, wherein all guide channels are provided with through-cuts in theworking surface of the cylinder with outlets into its cavity so thatlateral faces of the connecting rods of the synchronous groups of thedifferent directions facing the cavity of the cylinder form movableparts of its working surface, wherein the pistons are sequentiallyattached by their peripheries to the lateral faces of the connectingrods of the different synchronous groups, forming working chambersbetween them.
 2. The piston mechanism according to claim 1, wherein theconnecting members are disposed between the crankshaft and the pistonadjacent to it.
 3. The piston mechanism according to claim 2, whereinthe connecting members have the form of an inner and an outer connectingmember having central opening for free movement within one another sothat the outline of the inner connecting member repeats the outline ofthe central opening of the outer connecting member.
 4. The pistonmechanism according to claim 3, wherein the inner connecting member hasthe form of two plates joined to one another, a lower plate with a standand an upper plate with radial cuts around the periphery for theconnecting rod of the synchronous group of this connecting member,attached to the lower plate by their bases, and with recesses betweenthe connecting rods in both plates for the connecting rods of the othersynchronous group.
 5. The piston mechanism according to claim 4, whereinthe inner connecting member is joined with a middle crankpin of thecrankshaft.
 6. The piston mechanism according to claim 5, wherein theinner connecting member is joined with the middle crankpin of thecrankshaft through a central crank-hinge frame.
 7. The piston mechanismaccording to claim 6, wherein the central and lateral crank-hinge frameseach have the form of a separable rectangular outline and a slide bararranged within the outline for free translational movement engagingwith the corresponding crankpin of the crankshaft.
 8. The pistonmechanism according to claim 6, wherein the central crank-hinge framehas the stand joined with the stand of the inner connecting member via apin.
 9. The piston mechanism according to claim 8, wherein the centraland lateral crank-hinge frames are disposed between the guide platesarranged in the crankcase.
 10. The piston mechanism according to claim5, wherein the inner connecting member is joined with the middlecrankpin of the crankshaft via a central link.
 11. The piston mechanismaccording to claim 10, wherein the central link is joined with the standof the inner connecting member via a pin.
 12. The piston mechanismaccording to claim 3, wherein the outer connecting member has the formof two multi-faceted plates, having central openings, rounded to an ovalat their tops and attached to one another, the lower plate having twodiametric stands and the upper plate having radial cuts around theoutline of the central opening for the connecting rods of thesynchronous group of this connecting member attached to the lower plateby their bases and with recesses between the connecting rods in bothplates for the connecting rods of the other synchronous group.
 13. Thepiston mechanism according to claim 12, wherein the outer connectingmember is joined with two outer crankpins of the crankshaft.
 14. Thepiston mechanism according to claim 13, wherein the outer connectingmember is joined to the outer crankpins of the crankshaft throughlateral crank-hinge frames.
 15. The piston mechanism according to claim14, wherein each of the lateral crank-hinge frames has the stand joinedwith the corresponding stand of the outer connecting member via a pin.16. The piston mechanism according to claim 13, wherein the outerconnecting member is joined with the outer crankpins of the crankshaftthrough lateral links.
 17. The piston mechanism according to claim 16,wherein each of the lateral links is joined with the corresponding standof the outer connecting member via a pin.
 18. The piston mechanismaccording to claim 3, wherein three protrusions for attaching thepistons of one direction of movement are formed on the lateral faces ofthe connecting rods of the synchronous group of the inner connectingmember facing the cavity of the cylinder.
 19. The piston mechanismaccording to claim 18, wherein the protrusions on the connecting rods ofthe synchronous group of the outer connecting member are arrangedbetween the protrusions on the connecting rods of the synchronous groupof the inner connecting member.
 20. The piston mechanism according toclaim 18, wherein the protrusions on the connecting rods of onesynchronous group are provided at equal distance to one another which isequal to the distance between the protrusions on the connecting rods ofthe other synchronous group.
 21. The piston mechanism according to claim18, wherein the protrusions on the connecting rods of both synchronousgroup have increased area of their cross section.
 22. The pistonmechanism according to claim 18, wherein the pistons are provided withannular engaging grooves for the protrusions of the connecting rods ofthe synchronous groups.
 23. The piston mechanism according to claim 18,wherein the pistons are additionally attached to the protrusions of theconnecting rods of both synchronous groups by bolts.
 24. The pistonmechanism according to claim 3, wherein two protrusions for attachingthe pistons of the opposite direction of movement are formed on thelateral faces of the connecting rods of the synchronous group of theouter connecting member facing the cavity of the cylinder.
 25. Thepiston mechanism according to claim 1, wherein the connecting rods ofboth synchronous group are arranged with wide faces and shoulders forthe guide channels are arranged on the wide faces of the connected rodsfrom the side of their lateral faces which are furthest away from theaxis of the cylinder.
 26. The piston mechanism according to claim 25,wherein the shoulders are continuous.
 27. The piston mechanism accordingto claim 25, wherein the shoulders are interrupted.
 28. The pistonmechanism according to claim 25, wherein the width of the wide faces ofthe connecting rods of both synchronous groups exceeds the thickness ofthese connecting rods more than twofold in radial direction withoutconsidering the shoulders.
 29. The piston mechanism according to claim1, wherein the cross section of the connecting rods corresponds to thecross section of the guide channels.
 30. The piston mechanism accordingto claim 1, wherein the connecting rods are arranged in the guidechannels with a gap of less than 0.02 mm.
 31. The piston mechanismaccording to claim 1, wherein the pistons are provided with annulargrooves for sealing rings.
 32. The piston mechanism according to claim1, wherein the guide channels for the connecting rods of bothsynchronous groups cover the entire length of the working cylinder. 33.The piston mechanism according to claim 1, wherein the guide channelshave a T-shaped cross section profile.
 34. The piston mechanismaccording to claim 1, wherein the guide channels for the connecting rodsof the different synchronous groups alternate with each other by onechannel.
 35. The piston mechanism according to claim 1, wherein theguide channels for the connecting rods of the different synchronousgroups alternate with each other by two channels.
 36. The pistonmechanism according to claim 1, wherein the guide channels are formed inthe cylinder at equal distances from one another.
 37. The pistonmechanism according to claim 1, wherein the through-cuts in the guidechannels cover their entire length.
 38. The piston mechanism accordingto claim 1, wherein the inlet and outlet openings are located in themiddle sections of the working chambers formed by two diverging pistons.39. The piston mechanism according to claim 38, wherein the workingchambers are formed by diverging pistons and are equal in height. 40.The piston mechanism according to claim 1, wherein an additional workingchamber formed by one outer piston is two times smaller in height thanthe working chambers formed by the diverging pistons.
 41. The pistonmechanism according to claim 1, wherein the inlet and outlet openingsare arranged in the upper part of the additional working chamber formedby one outer piston.
 42. The piston mechanism according to claim 1,wherein the inlet and outlet openings are formed in spaces between guidechannels.
 43. The piston mechanism according to claim 1, wherein thecylinder is provided with an adjustable lid arranged on the crankcase.44. The piston mechanism according to claim 1, wherein the crankcasecomprises technical apertures.
 45. The piston mechanism according toclaim 1, wherein the cylinder is provided with a lid.
 46. The pistonmechanism according to claim 1, wherein the cylinder is provided withspark plugs in the working chambers.